Lathe



March 27, 1956 H. BECKER ET AL LATHE 4 Sheets-Sheet 1 Filed May 8, 1952 March 27, 1956 H. BECKER ET AL 2,739,501

LATHE Filed May 8, 1952 4 Sheets-Sheet 2 Inventor's. Han: Beckerand heo Mop o en,

March 27, 1956 H. BECKER ET AL LATHE 4 Sheets-Sheet 3 Filed May 8, 1952 4 8m? \N \N Q R Q a 5 Q 3&1 m? R. E KMPQJ, M .3 mm IHWNN U K? in Q% wm S w 0d, ml h. 6; a V c o 9 n he s o d, m x M H M w March 27, 1956 Filed May 8, 1952 H. BECKER ET AL LATHE 4 Sheets-Slieet 4 III Inventors.-

Hans Becker and Th 90 IVO aptfl,

By MfM Their 439/773.

LATHE Hans Becker, Dusseldorf, and Theo Noppen,

Dusseldorf-Heardt, Germany The invention relates to lathes for shaping the rolls of pilgrim step rolling mills.

With lathes of this type, the tool support during the shaping of the arcuate roll faces, as well as of the roll flanges, performs a rotary feed movement;-'at the same time, the tool carrier which is supported on a rectilinearly movable slide undergoes, in addition to the rotary feed movement, a linear feed displacement imparted to the slide by servo-motor means which are controlled by cams, during the shaping of the flanges.

With the known lathes of this type a special drumtype cam is provided which is rotated by a face plate drive and which produces the varying angles of the roll flanges, the said cam drum being differently shaped in its individual radial sections. During the working of the flanges, this drum which is rotatably located in a fork, is axially displaced by a threaded spindle driven from a rotary driving shaft, whereby the contour template for the basic movement as well as the tool holder receives a variable auxiliary movement at each rotation of the drum.

The manufacture of cam drums of this type is difiicult and expensive. Further, difiiculties arise from the interchange of the drums due to their insufiicient accessibility; considerable time is thereby consumed in setting up the machine.

These disadvantages are eliminated by the invention.

With this purpose in view, two or more cam discs are provided to produce the auxiliary movements of the tool slide required for effecting the turning of the caliber flanges, whereby the angular speed of at least one of these cam discs is dependent on the angular speed of the work and at least another is dependent on the extent of the tool displacement. By dividing the control drum into a number of simple control discs their construction is simplified and their manufacture is rendered extremely economical. At the same time, these control discs are ren dered easily accessible to the machine operator, v whereby they can be rapidly and freely interchanged.

Moreover, in conformity with this invention, the cam discs are coupled with each other by kinematic means in such a manner that the one cam disc imparts to the other one an additional rotation or displacement which causes an advance movement, or respectively a retardation, of said cam disc. This coupling is preferably effected by the interposition of a differential gear.

The foregoing and other objects of the invention will be best understood from the following description of ex-' emplifications thereof, reference being had to the accompanying drawings, wherein:

Fig. l is a front elevational view of the lathe; Fig. 2 is a sectionalview taken on line 2--2 of Fig. 1;

Fig. 3 is a sectional view taken on line 3-3 ofFig. 1,'

the driving motor being omitted;

Fig. 4 is a fragmentary sectional view taken on line 44 of Fig. 1;

Fig. 5 is a sectional view taken on line 5-5 of Fig. l;

Fig. 6 is a part sectional view taken on line 6-6 of Fig. 3; i

Fig. 7 is a schematic view that shows radial sections of the'roll caliber or forming roll in conformity with the indicators a-h in Fig. 2; and

i Fig. 8 is a sectional view similar to Fig. 5 but disclosing a modified embodiment of the invention.

in accordance with the first embodiment of the invention shown in the drawings, a work piece, such as a roll 1 (Fig. l) to be profiled, is driven from a motor 2 by means of gears 3, 4, 5 and 6. A pinion 8 is located on a shaft 7 and meshes with the gear 5 and transmits movement of rotation through a bevel wheel drive 9, 10 (Fig. 3) to a shaft 11, and thus to a cam disc 12 that is mounted on the shaft 11 and is disposed on the front face of the machine, as shown inFig. 1. The contour or curvature shape of this disc 12 corresponds to the shape of the cross-section of the finished roll 1. A cam follower 16 is located on a reciprocably movable carriage 15 (Fig. 4), and is pressed by a spring 13 (Fig. 1) into engagement with the cam disc 12; the stroke of the 'cam follower 16 is transmitted through a roller 17 to a rack l8which is connected to the roller 17. The roller 17 is disposed in a vertical groove 15a of the carriage 15, and is journalled on the rack 18. A pinion 20 that is mounted for rotation on a vertical ,shaft 19 meshes with the rack 18, and engages with a toothed rack 21 that is formed on a shaft 21a which is displaceably located in the bedplate of the machine. This rack 21 (Fig. 3) is of the type encircling the circumference of the shaft 21aand enables engagement with the pinion 20 in all radial positions of the pinion 20 relative to the axis of the shaft 21a. Said shaft 21a transmits power received from the rack 13 by means of a rack 21b of the shaft 21a, to a pinion 22 (Fig. 2) and to a vertical rack 23, thence to a pinion 24 and finally to a horizontal rack 25. The horizontal rack 25 is rigidly mounted on a 'slidable tool carrier 26 (Figs. 1 and 2) which is slidable in guides 27 on a carriage slide supporting device 28.

The said rack 23 is located concentrically of an axis x-x (Fig. 2), which is the axis of tool rotation as will be explained in detail below; and the rack 23 has a lower normal rack portion 23b which meshes with the pinion 22, and has an upper rack portion 23a which is of the encircling type, similar to the previously described rack 21 and which is in mesh with the pinion 24. This encircling typeupper rack portion 23a enables engagement with the pinion 24 in all radial positions of the pinion 24 relative to the axis xx By reason of the above-described transmission elements, all displacements of the cam follower 16 which are induced bythe cam 12, are positively transferred to the slidable tool carrier 26. The rotation drive 28 for turning the tool carrier 26 is effected by means of a worm drive that is concentric with the'axis xx to turn the tool about that axis, that includes a hollow gear 29 and a worm 30 (Figs. 2 and 5); said worm 30 is keyed on a shaft 31. Owing to the circular form of the upper rack portion 2311, it will be in engagement with the pinion 24 in all positions of the latter throughout the rotation of said pinion 24 about the axis xx, for continuous tool feed.

The shaft 31 extends with one end to the front exterior of the machine (Figs. 1; and 5)" and may be operated by hand with a crank or a hand wheel (not shown). The shaft 31 is furthermore operable to drive, by means a crank gear wheel 33 (Fig. 1); this crank gear wheel 33 imparts during each half rotation of the tool carrier 28, a to-and-fro movement to a movable rack 34 through a connecting rod 35, as best shown in Figs. 1 and 6. The connecting rod 35 ,is pivoted to the crank gear 33, and pivoted to the rack 34. The rack 34 is guided for sliding (Fig. 6), so that the rotation of the crank gear 33 brings about oscillation of the rack 34. The movement of the rack 34 is transmitted to a segmental rack 36 (Fig. l) and said segmental rack 36' transmits the movement to bevel gears 37, 33 and 39 (Fig. 3) of a diiferential gearing, the housing 40 of which is revoluh-le in the machine frame. From the dilferential gears the movement is then transmitted to a cam disc 41, which has a contour corresponding to the flange angle a and h of Figs. 2 and 7.

instead; of the aforementioned crank drive, which im parts a sine wave movement to the cam disc 41, it is possible to impart a uniform drive to the. cam disc, in accordance with the modification shown in Fig. 8. In. that modification, an. oscillating. drive is provided by pinions S1, 52,. 53 and pinions 54, 55 ad a. toothed clutch 56. The. pinions 51 and 54 of this oscillating drive are fastened onthe displacement shaft 31, and pinions 53 and 55. are; freely turnable on a shaft 57, which. is keyed to a pinion. 37 of the differential gear. The toothed clutch 56 is disposed to be revoluble with,v but. axially displaceable of the shaft 5.7 and between the pinions 53 and 55 engages: with corresponding teeth of the pinion 53 or 55,. as the case may be; it thereby transmits, according to its position, the revolution of the displacement shaft 31 either through the pinions 51,. S2 and 5-3, or in the opposite direction through the pinions 54, 55 on the shaft 57,. which. is mechanically coupled with the cam disc 41. A. l'ever linkage serves to set. thev position of the clutch. 5,. 6' and includes forked levers 60 and 61 that are pivoted on fixed pins 58 and 59,. and a connecting rod 62 that is connected to these levers 60, 61. The fork on the lever 61; cooperates with a pin. 63 on a worm wheel 64 whichis drivenby the worm 30.

Itwill thusv be seen that the worm wheel 64, in a given position of the lever 61, imparts a movement of oscillation which is transmitted by means of the connecting rod 62 to the. lever 60 which then displaces the clutch 56 into the. desired setting-up position for the tool carrier 26. Thev cam disc 41 thus receives in. the rotary displacement ofthe workcarrier from the right. hand side to the middleposition, an acceleration and during a displacement from the middle position. to the left, a retardation. The rotary movement of the cam disc 41 is thus. uniform and no longer of sine Wave form, as described in the first em- Y bodiment.

In either embodiments the cam disc 41 in its oscillation is. operable to alter the position of a cam follower lever 43 which is pressed into follower engagement by a spring 42. This lever 43' forms part of. a rotary oscillating member which is provided with. guides 43a. in the guides 43a is slidabl'y mounted the rack 18 which. controls the forward and backward feed of the tool. carrier 26 in the rotary movement of,.and transmit rotary movement to, the rotatable member. The rack 18 slidablymounted in the guides 43a is able to follow the movement of the cam follower 16 as transmitted. to it by means. of the reciprocable carriage 15,. the groove a. thereof, and the roller 17 that is carried bythe. rack. 18. and that is disposed in the. groove 15a and in motion-transmitting contact. with the sidewalls thereof. It; should, on the other hand, be borne in mind, that the carriage 15 is movable on the machine frame only: reciprocahlyg. for instance, horizontally as best shown in Figs. 1. and 3-.

impulses. transmitted to the. lever 43' by the cam disc 41 will therefore cause rotationalmovement of the mem ber 43, and thereby of the rack 18. Such rotationwill change the shortest distance between the center of rotation of the member 43 and the center of the groove 15a, resulting, owing to the positioning of the roller 17 in the groove 15a, in linear sliding displacement of the rack 18 relative to the guides 43a of the member 43. Thereby, the rack 18 will be linearly displaced, in addition to the displacement it is being subjected to by means of the action of the cam 12. and the cam follower 16. The pinion 20 the vertical shaft 19 of which. is arranged in the oscillating member 43 partakes in the rotational movement of the rack 18 and, as the axis of rotation of the member 43 coincides with the axis of the shaft 211:,

the pinion 20' will in all rotary positions of the raclcls be in mesh with the encircling rack 21 of the'shaft 21a. The auxiliary displacement of the rack 18 will be transmitted to the tool carrier 26 in the same manner as the normal displacement of the rack 18.

According to the present invention, the position of the lever 43 is not only controlled, as above described, by the turning displacement movement for the tool carrier 26, but. also by the rotary movement of. the work piece 1, This occurs in the arrangement shown, in that a further bevelv gear 45 (Fig. 3) is mounted on the shaft 7,. which drives a. bevel gear 46, which in turn drives a shaft 47 of a further camdisc 48.. This cam disc 48 has a cam follower 50, that is pressed into follower engagement by a spring 49;. the cam follower 50 extends from the housing 40. of. the difi'erential gearing. By this ar ra'ngement the cam disc 48 causes the follower 50 to oscillate and to transmit these oscillations through the ditfer ential gearhousing, 40 to the cam disc 41, so that. the latter receives an acceleration in the corresponding angular positions. of the worlcpiece 7 Instead ofv transmitting the movement positively, as

.in Fig; 2. Fig. 7 illustrates the linear feed movement to which. the. toolis subjected during its rotation, and

'which, carries. the changes schematically shown in this view from the impulse of. the cam discs 41 and 48 (Figs.

l, 3 adjusting the impulse from the cam 12. The proper profile is achieved by the cooperation of the earns 12,. 41 .-and.4s8, in imparting feed to the tool,

It will be: apparent to those skilled in the art that the novel principles of the invention disclosed herein in con:

nection; with specific. exemplifications thereof will suggest various other modifications andv applications of the same; It-is accordingly desired that in construing the breadth appended, claims they shall not be limited to the specific exemplifications of the invention described herein,

Having thus. described the invention, what we claim as new anddesire to. be secured by Letters. Patent, is as fellows-2.

L.. In a lathe,v for use in forming; flanged drawing: rolls of the type. used in flattening rolling mills, having a rotatable worlc piece; carrier and a power drive for the same, in combination with, a machine frame, a' table ro.-- tatably supported on said frame, rotating, means actuatableJformotating said table, a tool carrier sliding ra dially on said table and shiftablefor sliding. in opposite a mechanism ihclud'ing a second cam driven in. an oscillating motion from said rotating means in dependence fi'om: the'angnlar position of rotation of said table and being in operative connection with said cam follower imparting an auxiliary shifting to said slidable tool carrier for flange shaping, and an apparatus including a third cam driven by said power drive in synchronism with said work piece and being in operative connection with said second cam for impressing an additional motion on said second cam, in accordance with the angular position of rotation of said work piece.

2. In a lathe as claimed in claim 1, further characterized in that said mechanism and apparatus are revoluble, and said apparatus being in driving connection with said mechanism to impart thereto an auxiliary angular movement.

3. In a lathe as claimed in claim 2, further characterized in that said apparatus comprising a difierential gearing having a housing, and said driving connection including an extension of said housing to adjust the motion delivered by said differential gearing.

4. In a lathe, as claimed in claim 1, together with, said apparatus comprising a diiferential gearing having a housing, said table being in driving connection with said differential gearing, and said differential gearing being 6 in driving connection with said second cam, said third cam being in driving connection with the housing of said differential gearing for impressing an additional motion on said second cam.

5. In a lathe, as claimed in claim 1, said cam follower of said first cam including a slidable part in operative engagement with said follower, said second cam being in intermittent driving connection with said slidable part, whereby said cam follower will additionally be controlled by said second cam to transmit a composite feed motion to said tool carrier.

References Cited in the file of this patent UNITED STATES PATENTS 1,499,633 Becker July 1, 1924 1,894,899 Tschochner Jan. 17, 1933 1,918,138 Schimmel July 11, 1933 2,080,158 Yager May 11, 1937 2,109,454 Becker Mar. 1, 1938 FOREIGN PATENTS 573,712 Germany Mar. 16, 1933 

